Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H1/00—Toothed gearings for conveying rotary motion
  • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
  • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03D—WIND MOTORS
  • F03D15/00—Transmission of mechanical power
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
  • F03D—WIND MOTORS
  • F03D15/00—Transmission of mechanical power
  • F03D15/10—Transmission of mechanical power using gearing not limited to rotary motion, e.g. with oscillating or reciprocating members
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
  • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
  • F05B2260/00—Function
  • F05B2260/40—Transmission of power
  • F05B2260/403—Transmission of power through the shape of the drive components
  • F05B2260/4031—Transmission of power through the shape of the drive components as in toothed gearing
  • F05B2260/40311—Transmission of power through the shape of the drive components as in toothed gearing of the epicyclic, planetary or differential type
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E10/00—Energy generation through renewable energy sources
  • Y02E10/70—Wind energy
  • Y02E10/72—Wind turbines with rotation axis in wind direction

Definitions

• the present invention relates to a transmission unit according to the closer defined in the preamble of claim 1. Art.
• Transmission especially for wind turbines, are used to convert the torque and the speed between the transmission input and output shaft output.
• an applied at the transmission input shaft high torque is converted at low speed in a voltage applied to the transmission output shaft reduced torque at a higher speed.
• these transmissions can be divided into types of transmissions which have either planetary stages connected in series or planetary stages connected in parallel.
• differential gear which usually consists of three planetary stages.
• a transmission unit in particular for wind turbines, having a first, second and third planetary stage.
• the first planetary stage is arranged on the drive side, the third planetary stage on the output side and the second planetary stage preferably in the region between the first and third planetary stage in the transmission unit.
• the planetary stages each have a central sun gear, a ring gear surrounding this and radially arranged between these two planetary gears.
• the planet gears are rotatably supported in a planet carrier.
• the sun gears, planet carriers and / or ring gears of the planetary stage can be designed to be rotatable or stationary in the circumferential direction of the gear unit. In the latter case, they are rigidly coupled to a housing of the gear unit or as part formed of the housing.
• the three planetary stages are coupled with each other by means such that a drive-side rotational speed of the transmission unit can be increased on the output side.
• the means are designed to be rotatable about a rotational axis aligned in the longitudinal direction of the gear unit.
• the means may have a common axis of rotation, in particular a central axis of the gear unit, or else each comprise its own axis of rotation.
• the axes of rotation are aligned parallel to each other. Preferably, they are at least partially aligned coaxially with each other.
• the means comprise an output connection for coupling the second and third planetary stages.
• the output connection preferably rotatably couples the sun gear or the ring gear of the second planetary stage with the planet carrier or the ring gear of the third planetary stage.
• they form a unit rotatable about a common axis of rotation.
• the transmission unit can be made very compact. Furthermore, the design complexity of the transmission unit is reduced, so that it is cheaper to manufacture.
• the means for coupling the first and second planetary stage comprise a drive connection.
• the first and second planetary stage can be coupled together such that the coupled elements - sun wheel, planet carrier and / or ring gear - are able to rotate as a unit about a common axis of rotation.
• the transmission unit can be implemented very inexpensively, since the design complexity is reduced.
• expensive and error-prone bearings can be saved, so that the risk of failure of the gear unit is reduced.
• the sun gear of one of the two planetary stages is rotatably coupled by means of the drive connection with the planet carrier of the other planetary stage.
• the sun gear of the first planetary stage with the planet carrier of the second planetary stage or the planet carrier of the first planetary stage is rotatably coupled to the sun gear of the second planetary stage by means of the drive connection.
• the two ring gears of the first and second planetary stage can be coupled to one another in a rotationally fixed manner.
• a torque transmission from the first planetary stage to the second planetary stage take place.
• the construction volume of the gear unit is reduced by the coupling of the first and second planetary stage, since error-prone and expensive storage can be saved.
• a high speed translation can be realized in particular if the means for coupling the first and second planetary stage comprise two drive connections.
• each of the drive connections preferably couples different elements-sun gear, planet carrier and / or ring gear-of the two planetary stages with one another.
• the transmission unit can be implemented in a structurally simple manner, in particular, when the first of the two drive connections forms the sun gear of the first planetary stage with the planet carrier of the second planetary stage and the second drive connection forms the planet carrier of the first planetary stage with the sun gear of the second planetary stage as a rotationally fixed mutually coupled unit.
• the first drive connection couples the two ring gears of the first and second planetary stages and the second drive connection couples the sun gear of the first planetary stage with the planet carrier of the second planetary stage.
• the transmission unit can be made very compact.
• high translations can be realized quickly in a structurally simple way.
• the torques acting on the first and second planetary stages can be reduced, so that these planetary stages can be made very space-saving, since they have to withstand a lower torque.
• the means comprise an overall connection which rigidly couples the first, second and third planetary stages.
• the overall connection couples the three planetary stages to one another in such a way that in each case one element-sun gear, planet carrier and / or ring gear-of each planetary stage is designed to be rotatable about a common axis of rotation in the circumferential direction of the gear unit.
• the overall connection is the sun gear the first planetary stage with the sun gear of the second or third planetary stage and with the ring gear of the other of these two planetary stages rotatably coupled. Accordingly, the overall connection couples either the sun gear of the first planetary stage with the sun gear of the second planetary stage and the planet carrier of the third planetary stage. Alternatively, the overall connection couples the sun gear of the first planetary stage with the planet carrier of the second planetary stage and the sun gear of the third planetary stage.
• very high ratios can be realized quickly with minimal installation space of the gear unit.
• the overall connection rotatably couples the ring gear of the first planetary stage with the sun gear of the second planetary stage and the planet carrier of the third planetary stage.
• the ring gear of the first planetary stage, the sun gear of the second planetary stage and the planet carrier of the third planetary stage thus form a unit rotatable about an axis of rotation.
• the planetary gear torques can be kept low because the drive-side torque is divisible to all three planetary stages.
• the advantages of the above-described coupling of the overall connection to bear in particular when the drive-side torque is distributed to all planetary stages of the transmission unit.
• the gear unit can be designed to save space, since the three planetary stages each have to withstand a lower partial torque.
• the drive-side rotational speed of the transmission unit can be increased efficiently and effectively on the output side if the means for coupling the first and third planetary stage comprise a bridge connection.
• this couples the sun gear of first planetary stage with the planet carrier of the third planetary stage such that they are able to rotate as a unit about a common axis of rotation.
• the transmission unit can thus be made very compact.
• the planetary stages are coupled to one another in such a way that the drive-side torque can be distributed to at least two planetary stages, in particular the first and second planetary stages, and can be brought together in the third planetary stage.
• the drive-side torque can also be divided among all three planetary stages, in particular using the overall connection.
• the planetary stages can thus be made smaller, since they must withstand lower torque. As a result, the construction volume of the transmission unit is reduced.
• a division of the drive-side torque to a plurality of planetary stages can be implemented in a space-saving and constructive simple, if the drive connection or the overall connection on the drive side formed as a drive shaft or rotatably coupled to a drive shaft.
• the transmission unit can be implemented with a constructively low cost, cost-effective, lightweight, with low absolute and relative speeds, a very good gear efficiency, a high speed translation and compact design when the transmission unit, especially in the case of a completely introduced into the first planetary stage drive-side torque, two means, in particular an output connection, a drive connection and / or a total connection, has.
• the transmission unit has three means, in particular an output connection, a drive connection, a bridge connection and / or an overall connection.
• the gear unit can be structurally simple and robust implemented when the overall carrier is coupled to a drive shaft and / or the sun gear of the third planetary stage with an output shaft.
• the drive and output shafts are in particular arranged coaxially to one another and / or have the same direction of rotation.
• the third planetary stage in particular by means of its sun gear, is coupled to a spur gear stage.
• the spur gear can be designed such that the gear unit can be used in high-speed applications in wind turbines.
• the designated generator is operated at a rated speed of about 1 .550 1 / min.
• the spur gear can also be designed as a medium-speed application, in which a larger generator with a much lower generator speed of about 450 1 / min is used.
• the advantages of the compact design, the robustness at the same time high translation options come fully to fruition.
• 1 and 2 show two alternative embodiments of a transmission unit with two drive connections and an output connection in a schematic half-view
• FIG. 3 shows a schematic half-view of a third embodiment of the transmission unit with a drive connection, a bridge connection and an output connection,
• 4 and 5 is a schematic half-view of a fourth and fifth embodiment of the transmission unit with a total connection, a drive connection and an output connection,
• Figure 6 and 7 is a schematic half-view of a sixth and seventh embodiment of the transmission unit with a drive connection and an output connection and 8
• 9 and 10 show a schematic half view of an eighth, ninth and tenth embodiment of the transmission unit with a total connection and an output connection.
• each alternative embodiments of a transmission unit 1 is shown.
• the gear units 1 are provided in particular for wind power plants and each have a first planetary stage 2, a second planetary stage 3 and a third planetary stage 4.
• the first planetary stage 2 is arranged on the drive side in the region of a drive shaft 12.
• the third planetary stage 4 is formed on the output side in the region of an output shaft 18.
• the second planetary stage 3 is arranged between the first planetary stage 2 and the third planetary stage 4.
• Each of the three planetary stages 2, 3, 4 each have a central sun gear 5, 6, 7 and a ring gear 14, 15, 16 surrounding it.
• a plurality of planet gears are arranged, which mesh in a radially inner region with the sun gear 5, 6, 7 and in a radially outer region with the ring gear 14, 15, 1 6. Due to the schematic half-view, only one of the planetary gears 1 1, 12, 13 of each planetary stage 2, 3, 4 is shown in the figures.
• the planet gears 1 1, 12, 13 are held in the respective planetary stage 2, 3, 4 by means of a planetary carrier 8, 9, 10 in the radial direction of the transmission unit 1.
• the planet gears 1 1, 12, 13 are rotatably mounted in the respective planet carrier 8, 9, 10.
• the three planetary stages 2, 3, 4 are coupled with each other such that a low-speed drive-side high torque is converted into a high-speed output-side lower torque.
• the embodiments shown in Figures 1 to 10 differ from each other by the different couplings between their respective elements, ie their respective sun gears 5, 6, 7, planet carriers 8, 9, 10 and ring gears 14, 15, 1 6.
• the couplings are such coordinated that the transmission unit 1 is designed to save space. As a result, it has a lower weight, so that it can be used outstandingly especially in wind turbines.
• the different embodiments of the transmission unit 1 are characterized by a low design complexity, whereby the Production costs can be reduced.
• high speed translations with good gearing efficiencies, low absolute and relative speeds and low planetary gear torques are possible.
• the embodiments of the gear unit shown in Figure 1 to 5 form a first group in which the planetary stages 2, 3, 4 are coupled together such that the drive-side torque on at least two of the planetary stages 2, 3, 4 can be divided. On the output side, the divided torques are brought together either in the second planetary stage (FIG. 1 and FIG. 2) or in the third stage of the planetary stage.
• the embodiments of the transmission unit 1 illustrated in FIGS. 6 to 10 form a second group in which the drive-side torque is not divided among a plurality of planetary stages 2, 3, 4. Instead, in these embodiments, the entire drive-side torque is introduced into the first planetary stage 2.
• the transmission unit shown in Figure 1 has three means for coupling the three planetary stages 2, 3, 4. Accordingly, the first and second planetary stage 2, 3 with a first drive connection 1 9 and a second drive connection 20 coupled together.
• the first drive connection 1 9 connects the first planetary carrier 8 of the first planetary stage 2 with the second sun gear 6 of the second planetary stage 3.
• the second drive connection 20 couples the first sun gear 5 of the first planetary stage 2 to the second planet carrier 9 of the second planetary stage 3.
• the transmission unit 1 on a third coupling, which is designed as a driven connection 21.
• the output connection 21 connects the second ring gear 1 5 of the second planetary stage 3 with the third planetary carrier 1 0 of the third planetary stage 4.
• the first drive connection 1 9, second drive connection 20 and output connection 21 each form a substantially rotatable in the circumferential direction of the transmission unit 1 unit.
• the respectively coupled elements of the respective planetary stages 2, 3, 4 rotate at the same rotational speed in the circumferential direction of the transmission unit 1.
• the first drive connection 19 is coupled to the drive shaft 17 or designed as such in its drive-side region. Due to the first drive connection 19, the drive-side torque is distributed to the first planet carrier 8 and the second sun gear 6 of the first and second planetary stage 2, 3.
• the two planetary stages 2, 3 can be made very space-saving, since they have to withstand lower forces.
• the first ring gear 14 of the first planetary stage 2 is fixed.
• the first planetary carrier 8 is set in rotation such that the first planetary gear 1 1 rotatably mounted therein rolls in the stationary first ring gear 14 in such a way that the first rotor coupled radially inwardly therewith Sun gear 5 is set in a rectified to the drive shaft 17 rotation.
• the second planet carrier 9 consequently moves in a direction of rotation which is rectified to the first planet carrier 8 and to the drive shaft 17. Due to the transmission in the first planetary stage 2, the second planetary carrier 9 rotates faster than the first drive connection 19 and the second sun gear 6 coupled therewith. As a result, the second ring gear 15 engaged with the second planetary gear 12 in the radially outer region becomes second to the second Drive connection 20 offset rectified rotation.
• the third planetary gear 13 rolls in the fixed third ring gear 1 6 of the third planetary stage 4 from such that in the radially inner region with the third planetary gear 13 in engagement third sun gear 7 is set in a direction of the drive shaft 17 rectified rotation.
• the third sun gear 7 is coupled on the output side with the output shaft 18 or designed as such.
• the first and second planetary stages 2, 3 are likewise coupled by means of a first and second drive connection 19, 20.
• the first drive connection 19 is connected in a rotationally fixed manner analogously to the drive shaft 17 or on the drive side as a drive shaft 17.
• the second and third planetary stage 3, 4 with an output connection 21 in operative connection.
• the first drive connection comprises the first sun gear 5 and the second planet carrier 9. The drive-side torque is thus introduced via the drive shaft 17 in the transmission unit 1, wherein the first drive connection 19, the torque to the first and second planetary stage 2, 3 divides.
• the second drive connection 20 rotatably couples the first ring gear 14 of the first planetary stage 2 to the second ring gear 15 of the second planetary stage 3.
• the transmission unit 1 comprises the output connection 21, which drives the second sun gear 6 of the second planetary stage 3, as previously explained with the third planet carrier 10 of the third planetary stage 4 rotatably coupled.
• the first planet carrier 8 of the first planetary stage 2 and the third ring gear 1 6 of the third planetary stage 4 are fixed.
• the drive shaft 17, the first drive connection 19 and the output connection 21 rotate in the same direction.
• the second drive connection 20 rotates in the opposite direction.
• the first sun gear 5 and the second planet carrier 9 is set by means of the voltage applied to the drive shaft 17 torque in rotation, wherein the torque to the first and second planetary stage 2, 3 is divided. Since in the first planetary stage 2, the first planet carrier 8 is stationary, causes the first planetary gear 1 1, that the first ring gear 14 moves opposite to the rotational direction of the drive shaft 17. The same applies to the second ring gear 15, which is rotatably coupled by means of the second drive connection 20 with the first ring gear 14. As a result, the second planet carrier 9 and the second ring gear 15 rotate in opposite directions to each other, whereby the rotational speed of the second sun gear 6 meshing with the second planetary gear 12 is increased.
• the second sun gear 6 transmits the summed torque to the third planet carrier 10. This causes the third planetary gear 13 unrolls in the fixed third ring gear 1 6 and thus the third sun gear 7 in a rectified compared to the third planet carrier 10
• the illustrated in Figure 3 alternative embodiment of the transmission unit 1 also has three couplings.
• a first coupling is formed by means of a drive connection 19 between the first planet carrier 8 of the first planetary stage 2 and the second sun gear 6 of the second planetary stage 3.
• the drive connection 19 is coupled to the drive shaft 17 or designed on the drive side as such.
• the transmission unit 1 between the second planetary stage 3 and the third planetary stage 4 has an output connection 21 which rotatably couples the second and third ring gear 15, 16 of the second and third planetary stages 3, 4.
• the third coupling of the gear unit 1 is formed by means of a bridge connection 22, which bridges the second planetary stage 3 and thus couples the first planetary stage 2 with the third planetary stage 4.
• the bridge connection 22 comprises on the drive side the first sun gear 5 of the first planetary stage 2 and on the output side the third planet carrier 10 of the third planetary stage 4.
• a drive-side introduced torque is thus divided by means of the drive connection 19 on the first planet carrier 8 and the second sun gear 6.
• the first planetary gear 1 1 rotates in such a way that the first sun gear 5 is set in a direction rectified to the drive shaft 17 rotation.
• the third planetary carrier 10 thus also rotates in the same direction of rotation.
• the second planetary carrier 9 is fixed.
• the rotatably mounted in this second planetary gear 12 is driven by the second sun gear 6 such that the second ring gear 15 is set in a direction opposite to the first drive connection 19 rotation.
• the third ring gear 16 is offset due to the output connection 21 in a rectified to the second ring gear 15 rotation.
• the second planetary stage can be designed as a plus planetary gear set, if at the same time the connections to planet carrier and ring gear of the second planetary gear are reversed, ie the ring gear of the plus planetary gear is stationary, and the planet carrier is then connected to the ring gear of the third planetary stage.
• FIG. 4 shows an embodiment of the transmission unit 1, in which the three planetary stages 2, 3, 4 are coupled to each other analogous to the previous embodiments by means of three couplings.
• the transmission unit 1 has the drive connection 19, which couples the first planetary stage 2 with the second planetary stage 3.
• the drive connection 19 comprises for this purpose the first sun gear 5 and the second planet carrier 9.
• the output connection 21 is formed between the second and third planetary stages 3, 4, which couples the two ring gears 1 5, 16 of the second and third planetary stages 3, 4.
• the gear unit 1 has an overall connection 23, which forms the first ring gear 14, the second sun gear 6 and the third planet carrier 10 into a unit rotatable about a rotation axis.
• the overall connection 23 is on the drive side formed as a drive shaft 17 or connected to the drive shaft 17.
• the drive-side torque is thus divided by means of the overall connection 23 to the first, second and third planetary stage 2, 3, 4.
• the first ring gear 14 drives the first planetary gear 1 1 in such a way that the first sun gear 5 or the drive connection 19 rotates in an opposite direction compared to the drive shaft 17.
• the second planet carrier 9 and the second sun gear 6 rotate in opposite directions, so that the rotational speed of the second planetary gear 12 is increased.
• the second planetary gear 12 in turn meshes with the radially outer Shen arranged second ring gear 15 a.
• the embodiment shown in Figure 5 is substantially identical to the embodiment shown in Figure 2. As a difference, however, the second output connection 20 formed in FIG. 2 according to FIG. 5 is replaced by a total connection 23. This couples all three ring gears 14, 15, 1 6 of the three planetary stages 2, 3, 4 with each other, so that a rotatable unit is formed. In the exemplary embodiment illustrated in FIG.
• the third ring gear 16 is therefore also set in rotation due to the overall connection 23, which is opposite to the direction of rotation of the output connection 21.
• the rotational speed of the third planetary gear 13 is additionally increased, so that the output side, a faster rotating output shaft 18 is present.
• FIGS. 6 to 10 listed below have no drive-side distribution of the torque. Instead, the drive-side torque is introduced entirely into the first planetary stage 2.
• the first planetary carrier 8 is coupled to the drive shaft 17 or formed on the drive side as the drive shaft 17.
• the rotatably mounted in the first planet carrier 8 first planetary gear 1 1 thus rotates in the fixed first ring gear 14 such that in a radially inner region in meshing first sun gear 5 is set in rotation, the same effect to the rotation of the drive shaft 17 is trained.
• the embodiments illustrated in FIGS. 6 to 10 have only two couplings.
• the first coupling of the transmission unit 1 shown in FIG. 6 is designed as a drive connection 19, which rotatably couples the first sun gear 5 with the second planet carrier 9.
• the second planetary carrier 9 thus rotates in the same direction as the drive shaft 17. Since the second sun gear 6 of the second planetary stage 3 is stationary, the second planetary gear 12 also displaces the second ring gear 1 5 in a direction of rotation that of the second planet carrier 9 equivalent.
• the torque of the second ring gear 15 is transmitted to the third planet carrier 10.
• the third ring gear 1 6 of the third planetary stage 4 is stationary, so that the third planetary gear 13 rolls so that the third sun gear 7 in a direction of the drive shaft 17 rectified Rota tion is offset.
• the output shaft 18 is presently coupled to the third sun gear 7 rotatably.
• the first and second planetary stages 2, 3 are coupled in a rotationally fixed manner to a drive connection 19.
• the second and third planetary stage 3, 4 is in operative connection by means of an output connection 21.
• the output connection 21 in this case couples the first sun gear 5 to the second planet carrier 9. This rotates the second planetary gear 12 so that it rolls in the stationary second ring gear 15 in such a way that the second sun gear 6 is set in rotation.
• the torque of the second sun gear 6 is introduced by means of the output connection 21 in the third planet carrier 10. Due to the fixed third sun gear 7, the third ring gear 1 6 is rotated by means of the third planetary gear 13 in rotation.
• the third ring gear 1 6 is the output side formed as an output shaft 18 or rotatably coupled to the output shaft 18.
• the drive shaft 17, the drive connection 19, the output connection 21 and the output shaft 18 rotate in the same direction.
• the embodiment shown in Figure 8 also has two couplings, one of which is designed as a total connection 23.
• the overall connection 23 couples the first sun gear 5 of the first planetary stage 2, the second planet carrier 9 of the second planetary stage 3 and the third sun gear 7 of the third planetary stage 4. These therefore rotate in a direction of rotation corresponding to the direction of rotation of the drive shaft 17.
• an output connection 21 is formed, which in the present case couples the second sun gear 6 of the second planetary stage 3 with the third planet carrier 10 of the third planetary stage 4 in a rotationally fixed manner.
• the second ring gear 15 of the second planetary stage 3 is stationary, so that the second planetary gear 12, which is rotated by means of the overall connection 23, rolls in the second ring gear 15 in such a way that the second sun gear 6 meshing in the radially inner region is in mesh Rotation is offset.
• the third sun gear 7 and the third planet carrier 10 rotate in the same direction. Due to the translation in the second planetary stage 3, the third planet carrier 10 rotates in comparison to the third However, sun gear 7 faster, so that the third ring gear 16 is rotated in a direction rectified to the drive shaft 17 in rotation.
• the third ring gear 16 is rotatably coupled to the output shaft 18 or output side formed as the output shaft 18.
• the alternative coupling concept of the gear unit 1 shown in FIG. 9 substantially corresponds to the coupling concept of the gear unit 1 illustrated in FIG. As a difference, however, the output connection 21 between the second sun gear 6 and the third ring gear 1 6 is formed. As a result, the third ring gear 16 and the third sun gear 7 rotate in the same direction. However, since the output connection 21 rotates faster compared to the overall connection 23, the third planet carrier 10 is set in a direction rectified to the drive shaft 17 rotation.
• the three planetary stages 2, 3, 4 are likewise coupled to one another by means of an overall connection 23.
• the second planetary stage 3 and third planetary stage 4 are coupled by means of an output connection 21 which rotatably connects the second ring gear 15 and the third ring gear 1 6 with each other.
• the second planetary carrier 9 of the second planetary stage 3 is stationary, so that the second ring gear 15 and the output connection 21 is set in a direction opposite to the overall connection 23 rotation. Due to the output connection 21 thus also the third ring gear 16 and the third planet carrier 10 rotates in opposite directions. As a result, the rotational speed of the third planetary gear 13 or of the third sun gear 7 meshing therewith is increased.
• the third sun gear 7 is used here as the output shaft 18th

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• 2013
  • 2013-10-11 CN CN201380057244.7A patent/CN104781584B/zh not_active Expired - Fee Related
  • 2013-10-11 JP JP2015544387A patent/JP2015535582A/ja active Pending
  • 2013-10-11 WO PCT/EP2013/071229 patent/WO2014082783A1/de active Application Filing
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